Pressor.



G. F. DE WEIN.

PRESSOR.

APPLICATION FILED MAY 5. 1913.

1,203,315. Patented Oct. 31,1916.

2 SHEETSSHEET I I 4' 35 1- 1:2: I' C E 33 36 1--I|:=T i- TLJREINE ITNEESES L L I G. F. DE WEIN.

PRESSOR.

APPLICATlON HLED MAY 5, 1913. 1,203,315. Patented Oct-.31, 1916.

2 SHEETSSHEET 2.

ELDWER WITNESSES- GEORGE 13. DE WEIN, or MILWAUKEE, WISCONSIN,

MANUFACTURING COMPANY, or MILWAUKEE,

DELAWARE.

ASSIGN'OR TO ALLIS-CHALMERS WISCONSIN, A CORPORATION OF PRESSOR.

Specification of Letters Patent.

Patented Oct. 31, 1916.

Application filed May 5, 1913. Serial No. 766,237.

larly to improvements in regulating devices for such pressers. Within the meaning of the term presser is included all pumps, blowers, compressors and fans, either centrifugal Er non-centrifugal, and either radial or axial ow.

The object of the invention is.to provide means for regulating the operation of a presser of the impositive displacement type, the regulation of the driving motor of which is accomplishedprimarily by fluctuations in the discharge pressure from the presser or in the speed thereof, and secondarily by a flow device interposed in the fluid passage through the pressor, the secondary control serving to compensate for small inaccuracies in the primary control.

The invention is especially applicable to pressers of the impositive displacement type as distinguished from pressers of the positive displacement type in which a positive or substantially constant volume of fluid is displaced at each stroke or revolution of the pumping element.

The invention is furthermore particularly applicable to pressors which have to deal with conditions where it is desired to keep at a predetermined constant value, the rate of pumping generally expressed in weight per unit time and more specifically expressed as volume of free air in unit time. This is the case in blowers for blast furnace service where the pressure varies to meet varying resistances of the furnace under different conditions. In pressors applicable to such service, it is desirable to have the device capable of delivering air at a substantially constant rate of compressing, and it is an ob ect of the present invention to provide a sensitive regulating device whereby such desirable operation is secured.

A clear conception of an embodiment of the invention may be had by referring to the drawing accompanying and forming a part of this specification, in which the various parts are designated by suitable reference characters.

Figure 1 of the drawing is a diagra1nmaticview of a blower direct connected to a turbine, having the regulating system shown in section and regulating sure. Fig. 2 is a similar view, regulating primarily by speed.

Referring to Fig. 1, the turbine 30 is direct connected to the blower. 40 by means of a common driving shaft 36. It should. be noted that any other form of motor, such as-an electric motor, gas engine, or reciprocating engine, may be substituted for the turbine 30 without departing from the scope of the present invention. The main regulator shaft 31 is drivingly connected to the shaft 36 by means of bevel gears 32, 33, secured to the shafts 31, 36, respectively. The speed regulator is secured to the upper end of the regulator shaft 31 and has its collar rotatably and slidably journaled in an opening formed near the right end of a floating lever 7, and a stop flange 2 on said collar limits the sliding between the collar and the floating lever. The right end of the floating lever 7 is pivoted to the upper end of the link 73, the lower end of which link is pivoted to the left end of a floating lever 7 4. The left end of the floating lever 7 is pivotally connected to the upper end of the turbine power controlling motor rod 14;. The upper extremity of the valve rod 13 is pivoted to the lever 7 intermediate its ends. The right end of the floating lever 74 is pivoted to the upper end of the float rod 37. The float 39 is secured to the lower end of the float rod 37 and serves as a means responsive to the changes in the volume of the fluid entering the pressor or blower 40 through the inlet passage 38 for afiecting the power varying means, as will be later" explained. Itis not, .however, intended to limit the invention to the specific use of a float 39 for this purpose, as there are numerous other devices responsive to variation in flow of fluid and well known to those skilled in the art, for instance, a meter or a Venturi device, which might be utilized to primarily by presaccomplish similar results. I A cataract cylinder 3 has its piston 75 mounted on an intermediate portion of rod 37 and its by-pass pipe 76 is controlled by valve 7 7 The piston rod 8 is provided with vertical slot 4 at its upper end, the slot receiving a pin 5 located at a point intermediate the ends of floating lever 74. Intermediate the pin 5 and the right end of floating lever 74 is a series of weights 6 adjustable in amount and position and serving to normally retain the pin 5 at the lower end of the slot. The weights also serve to increase the stability of the float 39. The power controlling motor consists of a piston 28 reciprocable within the cylinder 27, the upper and lower piston chambers of which are connected respectively to lower and upper portions of the controlling valve casing 23 by means of pipes 26, 25. The lower end of the rod 14 carries a throttle valve 29 which controls the admission of fluid to the turbine 30 through the inlet 34. The piston valve is fixed to the rod 13 connecting to an intermediate portion of floating lever 7, as explained, and is reciprocable within the valve casing 23.

The controlling valve comprises a series of concentric valve disks 18, 19, 20, 21, 22, successively positioned along the valve stem 13. The valve disks 19, 21, in normal position cut off communication through the pipes 26, 25, between the upper and lower piston chambers respectively of the cylinder 27 and lower and upper portions respectively "of valve casing 23. The exhaust pipes 16, 17, leave the valve casing 23 frompoints nearer the mid portion thereof and on opposite sides of the valve disk 20. The fluid pressure inlet pipe '24, which receives a supply of high pressure fluid, preferably oil, from any suitable source, enters the valve casing 23 at points thereof adjacent the points of communication of the pipes 25, 26, to the casing and in the normal position of disks -19,- 21, just beyond their outer faces. The disks are so proportioned and positioned on' the valve and the points of communication of the various pipes to valve casing 23 so located, that, in moving the valve up, disk 20 will cut off exhaust pipe 16 before disk 21 admits pressure from inlet pipe 24; and disk 18,will cut oil admission of pressure from inlet pipe 24 before disk 19 permits exhaust of pressure through ex haust pipe 17;and similarly in moving the valve down, disk 20 will cut ofi exhaust pipe 17 before disk 19 admits pressure from inlet pipe 24; and disk 22 will cut oil admission of pressure from inlet pipe 24 before disk 21 permits exhaust of pressure through exhaust pipe 16. The by-pass pipe 15 connects theextreme end chambers of the valve casing 23.

The blower discharge pipe 35 is constantly in communication with the lower piston chamber of the pressure cylinder 11 by virtue of the pressure pipe 12. The helical compression spring 9 coacts with its upper end against the upper head of the cylinder 11 and with its .lower end directly against the piston 10, thus tending at all times to urge the piston 10 in a downward direction against the action of the blower discharge pressure which acts upon the lower surface of the piston 10.

' The operation of the device of Fig. 1 is as follows: For purposes of illustration it will be assumed that the blower 40 is operating normally at .corresponding speed, pressure, rate of blowing, and power, and that the various elements of the device are in the position as disclosed in the drawing. Assuming an increase to take place in the resistance at the furnace, which is connected with the blower discharge 35, the pressure in the discharge pipe 35 automatically rises and the speed of the blower automatically increases to a natural corresponding value. The rate of blowing simultaneously decreases a definite amount because the power as yet remains the same in amount. The increase of discharge pressure acting upon the lower surface of the piston 10, causes the piston 10 to move upwardly, compressing the spring 9 and raising the pin 5, and the .left end of lever 74. The upward movement I of the left end of lever 74 causes the right end of lever 7 to rise and swing about its left-end connection which at the time is momentarily stationarily fixed. As the lever 7 is swung, the actuating valve with its disks 18, 19, 20, 21, is raised by virtue of its connection with the lever '7 through the valve rod 13. This upward movement of the actuating valve permits exhaust from the lower piston chamber of the. cylinder 27 through,

pipe 25 and exhaust pipe 16. Simultaneously, the upper piston chamber of the cylinder 27 is brought into communication with the pressure inlet 24 through pipe 26.

Duringthe upward shifting of the actuating valve, fluid is by-passed from the upper to the lower casing chamber through the pipe 15. Piston 28 is therefore caused to move downwardly, opening wider throttle valve 29. At the same time the actuating valve with its disks 18, 19, 20, 21, 22, is restored to its normal position. serving to limit further opening of the throttle valve. The opening of the throttle valve 29 simultaneously increases the power and rate of blowing of the unitto substantially its former value while the speed'remains at a substantially constant value corresponding to the pressure which also is assumed to have remained at its augmented value corresponding to the assumed increase in resistance in the furnace. If the resistance at the furnace decreases, the pressure in the discharge ,pipe 35 decreases and the reverse action of the regulating mechanism takes place to close the throttle valve 29 the desired amount.

Slight differences in the rate of blowing not compensated automatically as above explained will be regulated by the float 39 and its coacting parts. Assuming the rate of blowing to thus decrease slightly, float 39 will descend, as will right end of lever 74 whose left end will be raised and through link 73, also right end of lever 7. The valve disks will be raised and in this way as before explained, throttle valve 29 will be wider opened. This will restore the rate of blowing to its normal value.

Excessive speed increase will bring collar 2 into action to raise the valve disks beyond a point where the motion of piston 28 will cease to compensate and return them to normal mid position. Continued rise of the valve disks will reverse the connections to cylinder 27 by feeding pressure through pipe 25 to the lower end thereof and exhausting from the upper end thereof through pipe 26 and exhaust pipe 17. This will cause piston 28 to rise and close throttle valve 29 thus serving as a safety stop to pre= vent dangerous speeds.

The device of Fig. 2 difiers from that of Fig. 1 in combining the initiating controlling conditions, speed and rate of blowing instead of pressure and. rate of blowing. The speed governor 100 is in this'case attached to an intermediate point of floating lever 174, and the connection is a pivotal one so as to be'positive for both upward and downward motion "of the collar. Weights 106 are placed on the upper end of rod 37 instead of on lever 74:, as here they serve only the purpose of increasing the sta bility of float 39. The operation is similar to that described for the device of Fig. 1.

Suppose increased resistance "is met in the furnace fed with air from the'blower. The pressure will naturally have to increase to overcome same and increased pressure has a corresponding increase of speed,which will automatically ensue and; because the power has not then been changed, the rate of'pumping will be decreased for the moment. The governor 100 however will elevate its collar to raise the valve disks through the linkage to cause the piston 28 to-move downwardly and open throttle valve 29 thus increasing the power and bringing back the rate of pumping to normal. Slight irregularities and inaccuracies in the rate of blowing may be controlled by float 39 in the same way as in the device of Fig. 1.

Excessive speed rise will. in either of the cases illustrated, be prevented when the compensating function of lever',"1j07 is exhausted,

by the stem 14 being stopped in open throttle direction of movement by engagement of the piston 28 with the lower end of the cylinder 27. Further upward movement of the actuating valve disks after the piston and cylinder end thus engage will then as before reverse the connection to cylinder 27 to close throttle 29.

It should be understood that it is not desired to be limited to the exact details of construction shown and described, for obvious modifications will occur to a person skilled in the art.

It is claimed and desired to secure by Letters Patent,

1. In combination, a pressor of the impositive displacement type, a motor, means connecting the motor to the pressor for driving same, means for varying the power of the motor, means controlled by the resistance presented in the pressor discharge for actuating the power varying means, and means controlled by changes in the rate of flow of the fluid entering the pressor for actuating the power varying means.

2. In combination, a pressor, a motor for driving said pressor, means for varying the power of said motor, means controlled by the resistance presented in the pressor discharge for actuating the power varying means to vary the power .directly as said resistance varies, and means controlled by changes in the rate of flow of the fiuidentering the pressor for actuating the power varying means. r

3. In combination, a pressor of the impositive displacement type, a motor, means connecting the motor to the pressor for driving same, means for varying the power of the motor, means controlled by the resistance presented in the pressor discharge for actuating the power varying means to increase the power when said resistance increases, and means controlled by changes in-the rate of flow of the fluid entering the pressor for actuating the power varying means.

4. In combination, a pressor, a motor for ance presented in the pressor discharge for varying the power of said motor, 'andmeans responsive to changes in the volume of fluid entering the pressor for regulating the power of said motor.

- 5. In combination, a pressor, a motor connected to the pressor for driving same, a regulator controlling said motor, means responsive to changes in the resistance presented in the pressor discharge for controlling the motor, and means responsive to changes in the rate of flow of the fluid entering the pressor for controlling said motor.

6. In combination, a pressor, a motor for driving same, a regulator for said motor, means responsive to changes in the resistance presented in the pressor discharge for modi- 7 In combination, a pressor, a motor for drlvmg sald pressor, a'regulator for sald motor, and combined pressor discharge resistance actuated means and inlet flow actuated means for regulating the power of said 15 motor.

In testimony whereof, the signature of the inventor is afiixed hereto in the presence of G. F. DE WEIN.

5 two witnesses:

Witnesses:

W. H. LIEBER, LULU H. BROWN. 

